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EP0386469B1 - Turbine à transmission par engrenages planétaires - Google Patents

Turbine à transmission par engrenages planétaires Download PDF

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Publication number
EP0386469B1
EP0386469B1 EP90102171A EP90102171A EP0386469B1 EP 0386469 B1 EP0386469 B1 EP 0386469B1 EP 90102171 A EP90102171 A EP 90102171A EP 90102171 A EP90102171 A EP 90102171A EP 0386469 B1 EP0386469 B1 EP 0386469B1
Authority
EP
European Patent Office
Prior art keywords
bearing
journal
rotor
hub rotor
hub
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90102171A
Other languages
German (de)
English (en)
Other versions
EP0386469A2 (fr
EP0386469A3 (fr
Inventor
Werner Bosen
Hans-Dieter Denz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Atlas Copco Energas GmbH
Original Assignee
Atlas Copco Energas GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Atlas Copco Energas GmbH filed Critical Atlas Copco Energas GmbH
Publication of EP0386469A2 publication Critical patent/EP0386469A2/fr
Publication of EP0386469A3 publication Critical patent/EP0386469A3/fr
Application granted granted Critical
Publication of EP0386469B1 publication Critical patent/EP0386469B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
    • F03B11/06—Bearing arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy

Definitions

  • the invention relates to a turbomachine with a gear housing, impeller, pin and a planetary gear with rotating ring gear, sun gear and at least three planet gears, which are rotatably mounted on bolts connected to the housing, the impeller and the sun gear being firmly connected to one another to form a hub rotor, wherein the pin consists of a rear, thick clamping pin part and a cantilevered, tapered bearing pin part which adjoins the clamping pin part by a pin shoulder, and wherein the tapered bearing pin part engages in a bearing bore of the hub rotor.
  • turbomachines in particular of the radial type, work in practice in supercritical operation, combined with high peripheral bearing speeds.
  • a sufficient service life of the planetary gear can only be guaranteed if oil-lubricated and oil-cooled plain bearings are used for the bearing of the hub rotor.
  • Oil-lubricated plain bearings generate considerable friction losses at the high peripheral speeds required in turbomachinery, which on the one hand have a negative effect on the efficiency of the planetary gear and thus on the entire turbomachine, and on the other hand involve a complex supply of cooling and lubricating oil.
  • the invention has for its object to provide a turbo machine of the structure described, which is characterized by simple and compact design and above all without changing the structural design to simple How a constructive influence on the critical speeds is possible.
  • the object is achieved in a turbo machine of the construction described above in that the pin and the ring gear of the planetary gear are rotatably connected by a roller bearing which is arranged on the rear clamping part of the pin, and that between the tapered bearing part of the bearing pin and the hub rotor a further bearing is arranged, the bearing distance of the further bearing in a range which is 0.4 to 1.2 times the center of gravity distance of the hub rotor center of gravity, likewise measured from the journal shoulder, can be determined with the proviso that the Operating speed is a safe distance from neighboring critical speeds.
  • a second bearing point on the tapered bearing part is not necessary.
  • the one used between three planet gears Sun gear not only functions as a drive component, but also serves as a bearing for the hub rotor.
  • the critical speeds can be changed by the dimensions of the journal part of the central axis and the hub rotor (length, wall thickness, diameter). Otherwise, there is the possibility of influencing the critical speed by selecting the bearing spacing (LL) in the specified range according to the invention.
  • the critical speeds in the constructive design can be influenced in a wide range by simple constructive measures which do not affect the basic structure. Structural constraints resulting from the critical speeds no longer exist in the turbomachine according to the invention.
  • roller bearings in particular preloaded angular contact ball bearings (spindle bearings)
  • spindle bearings can be used for the bearing of the high-speed hub rotor.
  • the preferred embodiment of the invention provides that the hub rotor is supported Bearing point has at least one rolling bearing and that the bearing distance is matched to the dimensions of the central axis and the hub rotor in such a way that the operating speed lies at a safe distance from adjacent critical speeds.
  • This embodiment in which the use of plain bearings is dispensed with, is distinguished by a particularly simple structure, which is advantageous in terms of investment costs and operating costs in terms of low power losses.
  • the hub rotor can be implemented constructively in various ways.
  • One embodiment provides that the impeller and the sun gear are arranged on a hollow shaft which is supported on the bearing point. At very high operating speeds of the turbomachine, it may be necessary to keep the tangential tension at the edge of the bore within the permissible range by minimizing the impeller bore.
  • an embodiment according to the invention is advantageous in which a sleeve is integrally formed on the impeller, with which the sun wheel is directly connected.
  • turbomachine according to the invention can be used both as a turbocompressor and as an expansion turbine.
  • turbomachine according to the invention is equipped with a radial run.
  • the basic structure includes a flying impeller 1 and a planetary gear 2 with gear housing 3, rotating ring gear 4, central axis 5, sun gear 6 and at least three planet gears 7 (FIGS. 1 and 2).
  • the planet gears 7 are rotatably supported on bolts 6, which are connected to the gear housing 3.
  • the central axis 5 is designed as a pin with a clamping pin part 9 and a projecting, tapered bearing pin part 10.
  • the clamping pin part 9 has a relatively large diameter and connects to the tapered bearing pin part 10 via the pin shoulder 11.
  • the ring gear 4 is rotatably supported by means of a roller bearing 12.
  • the impeller 1 and the sun gear 6 are firmly connected to one another to form a hub rotor 13 and are rotatably mounted on a bearing point 14 on the central axis 5.
  • the bearing point 14 is arranged on the tapered bearing pin part 10 at a bearing distance LL from the pin set 11 of the clamping pin part.
  • the bearing distance LL is 0.4 to 1.2 times the center of gravity distance LS of the hub rotor center of gravity 15, which is also measured from the pin shoulder 11.
  • the hub rotor center of gravity means the center of gravity of the hub rotor 13 formed from the impeller and sun wheel.
  • the bearing point 14 supporting the hub rotor is equipped in the exemplary embodiment and according to a preferred embodiment with roller bearings, the bearing distance LL being matched to the dimensions of the central axis 5 and the hub rotor 13 in such a way that the operating speed of the turbomachine is at a safe distance from adjacent critical speeds.
  • the bearing 14 is with two Ball bearings 16 mounted. Prestressed angular contact ball bearings are expediently used, ie precision ball bearings with little internal clearance, which are preloaded in the axial direction and thus run without play.
  • a sleeve 17 is integrally formed on the impeller 1, with which the sun gear 6 is directly connected.
  • This embodiment is favorable for very high operating speeds of the turbomachine. If the impeller 1 is exposed to smaller centrifugal forces, it has also proven useful to arrange the impeller 1 and the sun gear 6 on a hollow shaft 18, which is supported on the bearing point 14, which is preferably equipped with roller bearings (FIG. 2).

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)

Claims (4)

  1. Turbine à transmission par engrenages, comprenant un carter d'engrenages (3), une roue mobile (1), un tourillon (5) et un engrenage planétaire (2) avec une couronne tournante (4), une roue solaire (6) et au moins trois roues planétaires (7) qui sont montées de manière tournante sur des axes (8) solidaires du carter (3), la roue mobile (1) et la roue solaire (6) étant solidarisées de manière à former un rotor sur moyeu (13), le tourillon (5) étant constitué par une section de queue de fixation (9) postérieure de grande épaisseur ainsi que par une section de tourillon diminuée (10) en saillie qui se raccorde à la section de queue de fixation (9) par un épaulement de tourillon (11), et la section de tourillon diminuée (10) s'engageant dans un alésage de roulement du rotor sur moyeu (13), caractérisée par le fait que le tourillon (5) et la couronne (4) de l'engrenage planétaire (2) sont couplés de manière tournante par un roulement (12) monté sur la section de queue de fixation (9) postérieure du tourillon (5), et qu'un palier supplémentaire (16) est disposé entre la section de tourillon diminuée (10) du tourillon (5) et le rotor sur moyeu (13), la distance (LL) du palier supplémentaire (16) qui est de l'ordre de 0,4 à 1,2 fois la distance (LS) du centre de gravité (15) du rotor sur moyeu, également mesurée à partir de l'épaulement (11) du tourillon, pouvant être fixée à la condition que la vitesse de régime se situe à une distance de sécurité des vitesses de rotation critiques voisines.
  2. Turbine selon la revendication 1, caractérisée par le fait que le palier (16) entre le rotor sur moyeu (13) et la section de tourillon (10) est constitué par au moins un palier à roulement.
  3. Turbine selon l'une des revendications 1 ou 2, caractérisée par le fait que la roue mobile (1) et la roue solaire (6) sont montées sur un arbre creux (18).
  4. Turbine selon l'une des revendications 1 ou 2, caractérisée par le fait que la roue mobile (1) comporte une douille (17) conformée en une seule pièce avec celle-ci et avec laquelle la roue solaire (6) est couplée directement.
EP90102171A 1989-03-04 1990-02-03 Turbine à transmission par engrenages planétaires Expired - Lifetime EP0386469B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3907058A DE3907058A1 (de) 1989-03-04 1989-03-04 Turbomaschine mit planetenradgetriebe
DE3907058 1989-03-04

Publications (3)

Publication Number Publication Date
EP0386469A2 EP0386469A2 (fr) 1990-09-12
EP0386469A3 EP0386469A3 (fr) 1991-03-20
EP0386469B1 true EP0386469B1 (fr) 1994-04-13

Family

ID=6375583

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90102171A Expired - Lifetime EP0386469B1 (fr) 1989-03-04 1990-02-03 Turbine à transmission par engrenages planétaires

Country Status (3)

Country Link
US (1) US5106261A (fr)
EP (1) EP0386469B1 (fr)
DE (2) DE3907058A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1401662B1 (it) 2010-08-27 2013-08-02 Nuova Pignone S R L Dispositivo espansore multistadio assiale con ingranaggi, sistema e metodo.
US12168968B2 (en) * 2020-01-13 2024-12-17 Virginia Tech Intellectual Properties, Inc. Simultaneous ocean wave and current energy harvesting

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1648479A (en) * 1925-09-03 1927-11-08 Hilbert Henry Equalizing device for rewinding web paper
US1998778A (en) * 1930-12-12 1935-04-23 Eclipse Aviat Corp Supercharger
US2374829A (en) * 1941-09-20 1945-05-01 Bendix Aviat Corp Transmission
GB724531A (en) * 1951-06-14 1955-02-23 Garrett Corp Compressor and drive
DE1004929B (de) * 1953-10-30 1957-03-21 Amag Hilpert Pegnitzhuette A G Kreiselpumpe mit fliegend angeordnetem Laufrad
US2845054A (en) * 1954-09-15 1958-07-29 Bendix Aviat Corp Pneumatic engine starter
CH370862A (fr) * 1958-07-04 1963-07-31 Snecma Compresseur centrifuge
US3214990A (en) * 1962-12-27 1965-11-02 Worthington Corp Geared turbine
US3498424A (en) * 1967-10-02 1970-03-03 Verson Mfg Co Multiple speed mechanical transmission system
SU1101586A1 (ru) * 1983-04-08 1984-07-07 Всесоюзный научно-исследовательский и конструкторско-технологический институт компрессорного машиностроения Центробежна турбомашина

Also Published As

Publication number Publication date
EP0386469A2 (fr) 1990-09-12
US5106261A (en) 1992-04-21
DE3907058A1 (de) 1990-09-20
DE59005308D1 (de) 1994-05-19
EP0386469A3 (fr) 1991-03-20

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